Bundle packaging and wrapping machine



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BUNDLE PACKAGING AND WRAPPING MACHINE l2 Sheets-Sheet 12 4770mm x United States Patent BUNDLE PACKAGING AND WRAPPING MACHINE John T. Hayford and Donald S. Hayford, Paterson, N. .l.

Application September 26, 1950, Serial No. 186,714

20 Claims. (Cl. 1e0 2s The invention relates to an improved bundle and package wrapping and tying machine, and has particular reference to means for doubly wire wrapping and anchor tying varying sized bundles of newspapers and analogous collective packaging of bulk paper bundles of a similar nature at equi-spaced positions around said bundles wherein both wrapping ties are either effected simultaneously or wherein one wrapping and tying thereof is effective separately and individually and the second wrapping and tying action thereof is efiected by means of the reverse activation of the initial wrapping and tying mechanism by synchronized automatic means operative in a unit form of power driven actuating apparatus.

The invention includes the movements of compressing the bundle or package, straightening the perimeters or contour of the bundle per se, While disposed on a supporting table within the wire wrapping mechanism at two points on said bundle to effect the simultaneous double wrapping thereof, of tying by twisting the wire wrapping into com pletely twisted engagement while under compression and the straightening alignment of the laminations making up the bundle, of cutting the wire binder means by severing the free ends thereof and by finishing the severed wire ends by folding in said ends adjacent the twist or tied ends thereof automatically to effect thereby a closely aligned tie twist therefor.

The object of the invention resides in the providing of a dual type wire wrapping and tying device whereunder the wire is tightly wrapped and tied around a bundle while such bundle is under compression in order to reduce the size of the bundle and to securely wrap and tie same without in any way crazing or injuring the components of said bundle.

Another object of the invention lies in the providing of double wire binding, wrapping and tying a bundle of laminated components at equally spaced points thereon, and of twist-tying the ends thereof after the automatic severance of said wire into a flat tie-twist having no projections on the relative severed ends thereof during the compressed positioning of the bundle in said mechanism.

A further object of the invention is to provide a wire wrapping and tying machine arranged to doubly encompass a bundle by wires adapted to contact said bundle at relatively spaced locations thereon, wherein the ends of said wires are anchored so that said wrappings are held under tension and by reason of the bundle being under compression simultaneously effect the size reducing of said bundle and the protection of a' double and two-way wrapping and tying of said bundle.

A still further object of the invention is in the providing of apparatus wherein the wires for wrapping same envelops the bundle at separated points around the surface area of said bundle and are fed into such positions by first doubly tensioning the feeding of the wire thereto and of automatically tensioning said wires during the moment of the Wrapping and tying of said wires around said bundle.

Another object of the invention is to provide a mechanism to automatically and simultaneously doubly wire 2,749,837 Patented June 12, 1956 wrap and tie a bundle while under a compressing action wherein the ends of both wrapping strands of said wires are held under tension by automatic anchoring means and while under compressed double tension automatically cut the freeing ends of said wires at their twisted tying points and of automatically reverse twisting the severed ends of said wires to effect projectionless and flat-twist ties therefor.

An additional object of the invention further lies in the providing of a device of the character as defined wherein the wires are wrapped around a bundle in the same direction or in opposite directions, of compressing said bundle to render it more compact, and of automatically and simultaneously tensionably wrapping said wires around said bundle and of twist-tying both of said wire wrappings simultaneously or dis-simultaneously, and of cutting the slack ends of both wrappings simultaneously or dis-simultaneously with the completion of the twist-tying of said double wrappings.

Still another and further object of the invention is in the providing of a dual type wire bundle wrapping, binding and tying machine wherein the components comprising the bundle are first straightened in conformation and compressed by automatic positioning means and encompassed within a dual mechanism consisting of relatively spaced shuttling rings carrying means disposing the double strands of wire to effect the double wrapping of said bundle, and double automatic tensioning means for maintaining the positioning of the binding and tying media on said shuttling rings during the wrapping and twist tying moment of said media around said bundle.

An ancillary object of the invention is in the providing of a bundle wrapping and tying machine wherein each operable mechanism is set-up on a dual basis to ifect'the double wrapping and tying of a bundle by means of wire bindings and whereunder such dual mechanism may operate synchronously or alternately the connecting means for each component part being geared to permit said mechanism to operate in unison both in a clock-wise direction or one part in a clock-wise and the other part in a counterclock-wise direction or both parts in a counter clock-wise direction, any given direction of the wrapping and tying of said bundle being automatically actuated and controlled to provide a single operation to produce the dual form of wrapping and tying of a bundle or analogous object. i

A major object of the invention is in the providing of a dual type operating mechanism to effect a double wrapping and tying of a bundle such as newspapers and the like wherein synchronously operating shuttling rings wrap and tie a bundle at spaced points thereon during a single cycle of operation of the wire shuttling means during the automatic actuation and control of the wrapping and twist tying means in order to effect the single handling of said bundle.

Still another object is the providing of apparatus for the double wire wrapping and twist tying of such wires binding on bundles and the like wherein the machine as a unit comprises a portable supporting frame composed of a single vertical supporting structure apertured at its central body portion and having a shelf-like table arranged to receive the bundle, package, etc., primary wire feeding and compound tensioning means as it is taken from a supply coil or spool, secondary tensioning means for dual lines of wires as they are passed from the said primary tensioning means to a plurality of sheaves carried by said dual shuttling rings where said wires are held under double tension and in annularly encompassing disposal around the bundle to be tied, dual gripping means and wire cutting means on a transverse plane beneath said table at a point adjacent the freeing ends of said wires, geared transmission means for actuating said shuttling rings and said gripping and cutting means, pressure means for actuating said aforesaid mechanism, geared transmission means for rever'sing said shuttling rings, means controlling the activation of said wrapping and tensionable tying means to oscillate said shuttles in either synchronism clock-wise rotation, or alternately counterclockwise direction of rotation, and automatic control means for starting and stopping all or any one of said component activating elements comprised in the dual form of bundling and twist tying apparatus as described.

Still a further object of the invention lies in the providing of a bundle wrapping machine wherein the shuttling means carrying the binder means is mounted in dual arrangement and disposed on continuous bearing means therefor.

A further object of the invention lies in the providing of a bundle wrapping machine wherein the shuttling means constituting the binder encompassing mechanism is set up back to back in dual assembly and has cut in the peripheries thereof a series of helixially disposed grooves whereon an endless cable driving means is disposed from the driving sheaves therefor to effect a more positive and accurate driving media therefor.

. In the following we describe the general embodiment of the invention, the features thereof being more fully defined and claimed hereinafter in the claims forming part hereof.

In the drawings Figure 1 is a front elevation of the wire-tying machine with the sheet metal coverings removed, showing the relationship of the straightener, compressor, dual wire-laying rings, slack takeup and wiretensioning devices, and the main drive cylinder,

Figure 2 is a longitudinal section on line 2-2 of Figure 1, showing the disposition of the dual wire-laying mechanism, slack takeup units, drive mechanism and feed tables.

Figure 3 is a transverse section on a line 3-3 of Figure 1, with a fragmentary section through both table tops and the wire baskets, showing further the dual wirelaying rings and their attendant supporting structure, the slack takeup units, initial and second wire tensioning means, and the wire baskets.

Figure 4 is a transverse section on a line 4-4 of Figure 2, detailing the dual drive mechanism and showing the clutch and reversal mechanism to provide for alternatively tying single and double ties.

Figure 5 is a section on a line 5-5 of Figure 4, detailing the main drive shaft and mechanism.

, Figure 6 is a section on a line 6-6 of Figure 4, detailing the primary drive mechanism.

Figure 7 is a section on a line 7-7 of Figure 4, detailing the reversing drive shaft and mechanism.

Figure 8 is a schematic view of one of the upper and lower sheaves of the dual drive mechanism, showing the line of the wire rope drive.

Figure 9 is an enlarged section on a line 9-9 of Figure 5, showing the typical method of clamping one end of the wire rope drive.

Figure 10 is an enlarged section on a line 10-10 of Figure 1 detailing the wire-laying ring support structure and a typical wire guide sheave mounting.

Figure 11 is an enlarged fragmentary view on a line 11-11 of Figure 1, showing the method of clamping the wire rope on the wire-laying ring for positive driving.

Figure 12 is a section on a line 12-12 of Figure 11, further detailing the wire rope drive clamps.

Figure 13 is a fragmentary elevation of one face of the wire-tying machine, with all metal coverings removed, detailing the threading of the wire from the wire basket to the wire-tying mechanism.

Figure 14 is an enlarged view of the initial wire tensioning device shown at A in Figure 13, detailing the means of initially tensioning the wire.

, Figure 15 is a fragmentary section on a line 15-15 of Figure 14.

Figure 16 is a section on a line 16-16 of Figure 15.

Figure 17 is an enlarged section on a line 17-17 of Figure 3, detailing the second, electro-magnetic wire tensioning mechanism, shown at B in Figure 13.

Figure 18 is a rear elevation of the center plate assembly, showing the gripper head drive mechanism and twisting and cutting drive mechanism.

Figure 19 is an enlarged section on a line 19-19 of Figure 18, detailing further the gripper head drive mechanism and the twisting drive gears.

Figure 20 is an enlarged section on a line 20-20 of Figure 18, detailing further the twisting and cutting drive mechanism, not shown in Figure 19.

Figure 21 is a plan elevation of the dual tying mechanism, showing the back to back relationship of the two tying units.

Figure 22 is a front elevation of the tying mechanism, showing the relationship of a set of the gripping and twist ing heads.

Figure 23 is an end elevation, with the supporting structure removed, of the tying mechanism, showing further the provisions of dual tying and detailing the gripping mechanism of the gripper heads.

Figure 24 is an enlarged fragmentary section on a line 24-24 of Figure 21, showing the dual twisting mechanism and its drive mechanism.

Figure 25 is a section on a line 25-25 of Figure 22, showing the toggle action for gripping the wire.

Figure 26 is a section on a line 26-26 of Figure 21, detailing further the toggle mechanism.

Figure 27 is a view on a line 27-27 of Figure 21, detailing the cutting mechanism of the gripper heads.

Figure 28 is a section on a line 28-28 of Figure 27, showing further details of the cutting mechanism.

Figure 29 is a view, on a line 29 29 of Figure 21, showing the cutting cam mechanism of the twisting heads.

Figure 30 is an enlarged section, on a line of Figure 22, showing the wire chip elimination means.

Figure 31 is an enlarged section, on a line 31-31 of Figure 22, showing further the wire chip elimination means.

Figure 32 is a detail view of a finished twist of the wire ends.

Figure 33 is a schematic layout of the pneumatic system for operation of the wire-tying machine.

Figure 34 is a partial schematic layout of the electrical system for operation of the wire-tying machine.

Figure 35 is a continuation of the schematic layout o the electrical system for the operation of the Wire-tying machine.

Similar reference characters indicate corresponding and like parts of the apparatus throughout the several views of the drawings forming part hereof.

With reference to Figure 2 of the drawings, the material to be packaged is fed into the machine opening, into position across the wire gaps, the movement facilitated by the rollers 2 built into the tables F and G. Table F is typical of a non-powered table where the bundle must be pushed by hand by the machine operator. Table G is typical of a powered table, where the bundle is carried on a plurality of tapes 5, supported over rollers 2, driven by a suitable electric motor 6. Both tables are supported by arms 7 pivoted about shafts 8, so that they may be moved back and down, as at F, for access to the rest of the machine mechanism. The tables are locked in the up position, as at G, by handles 9, Figure 3. Loose, bulk material to be packaged is furnished easy entrance to the machine opening by guides 10, Figures 2 and 3.

Both front and rear tables, F and G respectively, con tain limit switches to indicate the positioning of a bundle within the machine opening preparatory to tying; table F carrying LS1, which when actuated indicates a bundle bridging the front wire gap; and table G carrying LS2, which when actuated indicate a bundle bridging the rear wire gap. In addition, the rear table, G, also carries bundle position switches, LS16 and LS17, used in the motorized, automatic machine to indicate the correct positioning of the bundle, and to initiate the wire-tying sequence, as is hereinafter described. All limit switches are plunger actuated by conventional spring-loaded means.

Referring to Figures 1 and 3, the bundle to be packaged is straightened and held for the duration of the tying cycle into a neat, compact stock by the movement of the straightener head 11, carried on shafts 12 in a'plurality of bearings 13, and powered by cylinder C1. The bundle is racked up against side bars 15 supported at 16 on the ring supporting structure 17, which in turn is mounted on the main machine frame 1.

Referring to Figures 1 and 3, the bundle to be packaged is compressed and held down on the table 28, Figure 13, by compressor head 18, carried on vertical rods 19 by a plurality of bearings 20. The head 18 is powered through cylinder C2, mounted in supporting bracket 22 and attached to the main frame 1. The rods 19 are carried in sockets 23 in the frame 1 and sockets 24 in the bracket 22.

Referring to Figures 1 and 3, the bundle to be packaged is shaped at the corners, when necessary to prevent cutting by the wire, by the curved edge 3 of 11, the formed plates 25 and 26, carried on 18, and the curved block 27, mounted on 15. This curved block 27 also carries the bundle position switch LS3, actuated by the movement of the spring-loaded block 110 as the bundle is straightened and moved up against the side bars 15.

The bundle 14 to be wire-tied is now straightened, compressed and supported by tables F and G, Figures 2 and 3, and table 28, as in Figure 3, and lies across the wire gaps preparatory to being wrapped with the wire strand(s). The dual wire-laying rings, the front one 29, and the rear one 21, carrying a plurality of wire guide sheaves 30, are driven through an angular rotation of 1% revolutions, alternately clockwise and counterclockwise, by the drive mechanism, as hereinafter described.

Figures 3 and 13 indicate the path of the wire, from the wire coils 31 through the initial wire tensioning device at A to the second tensioning device at B to the slack takeup mechanism, consisting of the plurality of sheaves 32 at C, up across the plurality of pulleys 33 mounted on the frame 1, to the plurality of wire guide sheaves 30, through between the wire-laying sheaves 4, to end, for the position of 29 shown here, at the gripper head at D under the bundle 14.

Referring to Figure 13, the front wire-laying ring 29 is shown in a typical starting position. It will rotate clockwise during its next cycle. The wire is held in the gripper head at D, which has been moved out to straddle the wire line, through an action hereinafter described. During the initial wire-laying cycle the gripper head at E is back behind the wire line, so that wire may be laid without interference to the left and up around the left side of the bundle. The slack wire that is given olf during the ring rotation, until the wire-laying sheaves 4 reach the top vertical position, is taken up by the outward travel of the sheaves 32, mounted on traveling supports 34 which in turn slide in bearings on rods 35. These traveling supports are driven outwards by cylinders C8 and C9. The wire sheaves 32 are hooded by semi-circular pieces 36, to prevent the wire from jumping out of the sheave groove. The wire tension during this portion of the wire-laying cycle is determined primarily by the air supply pressure to cylinders C8 and C9.

As the ring 29, Figure 13, continues its rotation wire is laid to the right across the top of bundle 14 and down the right hand side. During this time the wire required is drawn from the slack takeup mechanism C, by the reduction of the sheaves 32, towards each other. Wire is tensioned during this portion of the cycle by back pressure of the air in cylinders C8 and C9, as hereinafter described.

The final portion of the wire-laying cycle requires wire to be drawn from the supply coil. As the ring lays the wire down to the left across the bottom of the bundle 14 the gripper head at D is drawn back behind the wire line and the gripper head at E is advanced out into the wire gap, by a mechanism hereinafter described. The wire is drawn up into the gripper head at E as the ring comes to a stop at the end of its cycle. The wire is tensioned during this portion of the cycle by the electromagnetic tensioning unit B and the initial, spring-loaded tensioning unit at A, later described.

Referring to Figures 2, 3, and 10, the dual wire-laying rings 21 and 29, both carrying a plurality of wire-guide sheaves 38 and two wire-laying sheaves 4, mounted on bearings 38 and carried on studs 39, are mounted in parallel planes on twin annular structures 17, bolted to the main machine frame 1 with bolts 37. The annular rings 21 and 29 run in a T-slot formed by bolting a retaining ring 40 to the ring structure 17 with screws 41, forming a circular track carrying, guiding, retaining and assembling the wire-laying rings.

The outside periphery of the wire-laying rings are cut with semi-circular grooves in the form of a helix, further pictured in the schematic detail, Figure 8, in which lies the wire-rope 42, that drives the wire-laying mechanism. This wire rope is clamped at its center, by the deforming action of the clamp 43 and screws 44, as shown in Figures l1 and 12, acting in a slot cut in the periphery of the rings at a point diametrically opposite the wire-laying sheaves. The object of the helical grooves for carrying the wire rope is to permit the Wire-laying rings to rotate alternately clockwise and counterclockwise on each successive cycle, the wire rope winding on and off the rings to the lower drive sheaves, as hereinafter described, during such rotation, and prevented from slipping by the clamp 43, to secure positive driving action.

Referring to Figures 1 and 4, the wire rope 42 is led off the wire-laying rings 29 and 21, down around the eccentrically mounted sheaves 45, to and around the lower drive sheaves 46 on the front face of the machine, and 47 on the rear face of the machine, respectively. The wire rope is wound around the drive sheaves 46 and 47, which again carry semi-circular grooves in the form of a helix on their outside periphery, in a manner pictured schematically in Figure 8, the two ends of the wire rope being clamped by passing down alongside and under the rim of the drive sheave and secured by clamp 48, held with bolts 49, Figure 9. Side plates 232, and screws 233, prevent the wire-rope from jumping out of the groove while passing alongside the rim of the sheaves 46 and 47.

Referring to the schematic diagram, Figure 8, of a typical wire rope drive, the wire is clamped at the left hand outside edge of the lower drive sheave, point A, lies in the helical groove until it is taken off at D to sheave 45, not shown, passes up into the upper wirelaying ring grooves at B, follows the helical grooves, is clamped at C, taken off at B to pass down to second sheave 45, not shown, to again wind around, in the helical grooves of the lower sheave until it is clamped at A, on the right hand outside edge, directly opposite A. On the next wire-laying cycle, the drive sheave will rotate, when viewed from the right to the left, as indicated, in a clockwise direction, driving the wire-laying ring clockwise, by Winding the rope onto itself from D to D, thereby taking it from the wire-laying ring from B to B; concurrently, the drive sheave will give up rope from D" to D' to the wire-laying ring from B to B. On the next cycle in the opposite direction, the reverse winding action takes place.

Referring to Figure 4, the sheaves 45 are eccentrically mounted on bearings 48, clamped and held with studs 49 to the main structure 1, to allow for taking up the slack on the wire-rope forming the drive. The sheaves 45 are so mounted as to have a freedom of motion axially, to permit their beingmaintained in line with the wire rope, as it travels axially in the helical grooves of the drive system.

Referring to Figures 1, 5, 6 and 7, the primary motive power for the drive mechanism is furnished through the double-rod ended cylinder C3, driving rack 50, meshed with pinion 51, through the adaptors 52 and bolts 53 and 54. The rack 50, guided in the bearing structure 55, carries bearing plates 56 riding on guide-ways 57; it also bears on bearing plate 58, mounted below pinion 51 in the structure 55. Bearing structure 55 is supported on, and bolted with 59 to stanchions which are a part of the base 60 of the machine structure. On each successive tying cycle the cylinder C3 is driven from one end position to the other, the reversal of direction of the cylinder travel imparting the reversal to the direction of rotation of the wire-laying rings.

Referring to Figure 4, the main drive pinion 51, keyed to shaft 61 with key 62, is mounted in the split bearings 63 by caps 64 and screws 65, on the bearing structure 55, and covered with hood 66 to further protect the gear and rack from foreign matter. One end of the shaft 61 carries gear 67 meshing with gears 68 and 69 on the main and reversing drive shafts, as hereinafter described; the other end of the shaft 61 carries a plurality of cams 238 for actuation of microswitches LS5, LS6, LS7, L812 and L813, hereinafter described.

Referring to Figures 4 and 5, the main drive shaft 70, driven by gear 68 in mesh with gear 67, is carried in bearing 71 on the bearing structure 55 and bearing 72 on the rear bearing structure 73; shaft 70 carries the front drive sheave 46 keyed to it, and has mounted upon it the rear drive sheave 47, in bearings 74 and 75, and the male, flat-faced, multiple-jawed clutch 76 on the feather key 77. In this arrangement the front drive sheave 46 is driven during each tying cycle of the machine; the rear drive sheave 47 is driven only upon the option of the operator through the clutch mechanism, hereinafter described.

The front drive sheave 46 has mounted on it a conventional electric brake armature 78 in contact with a conventional electric brake magnet 79. Magnet 79 is mounted, through support 80 and screws 81 to the front bearing structure 55. The sheave 46 also carries pinion 82 secured with screws 83 on its inner face, such pinion being the primary power source for the front gripper head drive mechanism, hereinafter described.

The rear drive sheave 47 has mounted on it a conventional electric brake armature 84 in contact with a conventional electric brake magnet 85.

Magnet 85 is mounted on the rear bearing structure 73. The sheave 47 also carries pinion 87 secured with screws on its inner face, such pinion being the primary power source for the rear gripper head drive mechanism, hereinafter described. In addition, sheave 47 carries the ring gear 89, and the female flat-faced multiple-jawed clutch 90, secured with screws 91. The installation of 47 on bearings over shaft 70 permits its rotation in a direction opposite to that of 46, or not at all, as is required occasionally, or is necessary in the case of singletie operation, as is hereinafter described.

Referring to Figures 4 and 7, the reversing drive shaft 92 driven by gear 69 in mesh with gear 67, is carried in bearing 93 on the front bearing structure 55 and bearing 94 on the rear bearing structure 73; has mounted upon it the reversing gear 95, in bearings 96 and 97, and the male, flat-faced multiple-jawed clutch 98 on the feather key 99, this clutch identical with 76 on the main drive shaft. In this arrangement the reversing gear 95, in mesh with 89, is driven only upon the option of the operator through the clutch mechanism hereinafter described.

The reversing gear 95 carries the female fiat-faced multiple-jawed clutch 100 mounted by screws 101.

Referring to Figures 4, and 7, the main and reversing clutches, mounted on the main shaft 70 and the reversing shaft 92 respectively, and powered by cylinder C9 and cylinder C10 respectively, both operate in identical fashion. The male clutch is engaged or disengaged through the toggle operation of arms 102, pivoted at the clutch housing 103, the yoke 104 and the bearing structure pivot 105. The clutch housing 103 is mounted over bearing 106, retained by rings 107 and 108, to permit axial leads transmitted to the clutch itself for engagement and disengagement and at the same time permit the continued rotation of the clutch itself within the housing. At the bearing structure 73 the arms 102 are pivoted about stud which is eccentrically mounted to permit alignment and positioning of the toggle mechanism.

For the purpose of clarity and description the main clutch is here shown disengaged, while the reversing clutch has been drawn in the engaged position. However, when the main clutch 76 is meshed with its mate 90, the rear drive sheave 47 is driven through the shaft 70 and key 77 in the same direction as the front drive sheave 46.

When the reversing clutch 98 is meshed with its mate 100 the rear drive sheave 47 is driven through the gear train consisting of 89 and 95 from reversing shaft 92 through key 99 in the opposite direction from the front drive sheave 46.

When both clutches are disengaged the rear drive sheave will not rotate, regardless of the direction of rotation of the front drive sheave. At no time may both main and reversing clutches be engaged together, this feature being taken care of through the electrical control system as hereinafter described. The rear drive sheave 47 is designed larger in diameter than the front one 46 so that the rear wire-laying ring 21 completes its wire-laying cycle before the front ring 29, permitting the disengagement and over-riding of either clutch some slight mount. Upon re-cycling, the correct clutch is reengaged, the faces will slip until correct meshing is obtained, and the rear wire-laying ring is driven. Without this feature the drive and clutch mechanism requires precision machining and position indexing not readily obtainable.

The rear bearing structure 73 supporting bearing 94 carries supports for pivotally mounting trunnion cylinders C9 and C10, and is in turn mounted on stanchions on the base 60 with screws 109.

Referring to Figure 3, one of the principal features of the machine is the means of storing, uncoiling, feeding, tensioning, and controlling the wire supply for the bundling. The two coils 31, front and rear, are held in a common basket 111 on the right hand side of the machine, retained and maintained in coil form by the inside, flared circular members 112, retained by the handles 113. Both coils are covered and protected and the wire prevented from kinking by the semi-circular, cone-shaped covers 114, as it is drawn from the coil through the initial tensioning device at A, Figure 13.

Referring to Figures 14, 15 and 16, the initial wire tensioning means shown at A in Figures 3 and 13 receives the wire from the supply coil 31 and passes it through the circular orifice formed by the two sheaves 115 rotatably mounted on shafts 121 so as to project through the side frame of the machine. The wire is passed between the three balls 116, carried in the retainer 117, loaded by spring 118. The three balls provide a pinching action on the wire, by the action of the spring-loaded retainer 117 and the tapered socket 119 built into the body of the tensioning device. The amount of pinch. or drag, on the wire, is determined by the spring load and the taper angle, the spring load being adjusted through the screwed piece 232 locked in position by nut 120. This initial tensioning of the wire is used to straighten out the wire from the supply coil and provides a slight braking drag on the wire as it passes to the second, main tensioning device.

Referring to Figure 17, the second, main electro-magnetic tensioning unit, shown at B in Figure 13, consists of a drum 122 about which the wire is wound one ormore turns, rotatably mounted on shaft 123, carrying a conventional electric brake armature 124 on pins 125 in spring-loaded contact with a conventional electric brake magnet 126, mounted on support 127 by screws 128, the entire unit mounted on the slack takeup base 129 by screws 130. The magnitude of the magnetic field, determined through the electrical control system as hereinafter described, determines the braking torque acting on drum 122, which in turn determines directly the wire tension. Thus the wire tension can be quickly, directly, positively controlled at all times under all conditions during the tying cycle. To prevent the wire from slipping around the drum rather than turning the drum a slight tension must be established in the wire leading onto the drum, this tension imparted through the initial wire tensioning device, heretofore described.

Referring to Figures 18 and 19, the front and rear gripper heads drive mechanism, which advances or Withdraws, the gripper hands to or from the wire line -of the wire-laying rings is pictured in detail; Figure 18 being an elevation of the rear gripper head drive mechanism, the opposite side for the front head being identical; and Figure 19 being a section through the mechanism indicating the dual construction. The main drive pinions 82 for the front drive mechanism and 87 for the rear drive mechanism, driving from 46, the front drive sheave, and 47, the rear drive sheave respectively, supply the primary motive sources for the drive mechanisms.

The gripper head drive arms 131, pivotally mounted on shafts 132, are driven by cams 133 through the eccentrically mounted cam followers 134, screwed into the ends of 131 and secured by nuts 135. This eccentric mounting of the cam follower permits correct alignment and positioning of the gripper heads. The cams 133, integral with gear 145, rotate on bearings 136, independent of each other, on the fixed shaft 139, held secure by the retaining ring 138. Gear 145 is part of the gear train consisting of the integral cluster gears 146 and 137, and gears 82 or 87, thus being positively tied to the rotation of the front and rear drive sheaves respectively. The cluster gears 146 and 137 are integrally mounted, independently of each other, on bearings 138 over the fixed shaft 139 and retained by rings 140 and 141 (Figure 19). The above described gear train reduces the rotation of gear 82 or 87 from their normal 2 /2 rotations per wire laying cycle to /2 rotation of the cam per wire-laying cycle, thus advancing or retracting either the left or right gripper heads, once each cycle of the wire-laying ring, as required, and as heretofore described. The upper ends of the gripper head drive arms 131 engage pin 141 in the gripper heads, as shown in Figure 27. The entire drive mechanism mounts on plate 142, which is adjusted for correct gear meshing between 82 or 87 and 137 by screws 143, and which is held to the main frame 1 through screws 144.

The independent mounting of the front and rear drive mechanisms insures the correct timing always being preserved between the gripper head position, i. e., in or out, and the wire-laying rings, for, when the rear drive sheave is declutched and held from rotating, as is the case during single tie' operation, the rear gripper head drive mechanism is likewise held from moving.

One gripper head drive arm 131, on each side of the machine, carries pin 147 to actuate, on the rear side, limit switch L815, the rear gripper head position switch, its function is hereinafter described. On the front side the pin 147, shown in Figure 18 and as located on an oppositely positioned drive arm for the sake of clarity, whereas actually the two mechanisms are located back to back, actuates limit switch LS14, the front gripper head position switch, and in addition, LS4, a drive position switch, the functions of which are hereinafter described.

Referring to Figures 18, 21 and 22, Figure 21 is a plan view of the dual tying mechanism, showing the relative back to back location of the gripping and twisting heads. For clarity and description the front right gripper head at H is shown out, the front left gripper head at H shown retracted, as it must always be in opposition to its mate; and the front twister head at J is shown retracted. Likewise, the rear right gripper head at K is shown out across the wire line, the left rear gripper head at K is shown retracted, and the rear twister head at L is shown advanced astraddle the wire line. All of the tying heads are carried in dovetail bearing devices, members 148 riding in the dovetail slots at M in the tying structure 149, the gripper head drive mechanism heretofore described and the twister head drive mechanism hereinafter described actuating the heads as is required.

Referring to Figures 13 and 22, Figure 13 shows the wire initially held beneath the bundle and running to the right to the wire-laying sheaves 4, while Figure 22 shows the wire position after the wire-laying cycle has been completed. Where the wire was initially held at K in the out position and running to the right, it now is held at K retracted, passes around the bundle 14, and at K advanced, and runs to the left to the wire-laying sheaves 4, not shown, on the ring 29 in its position at the end of the wire-laying cycle. In reversing the direction of rotation of the wire-laying ring each successive cycle a small hair pin shape of wire, shown here at K, is produced alternately in each gripper head. As is seen, at the conclusion of the wire-laying cycle the wire strands wrap the bundle and lie crossed in front of the twister head L, preparatory to being straddled by the slotted twister gear and knotted, as hereinafter described.

Referring to Figures 21, 22, 23, 25 and 26, the gripping action for holding the wire strands consists of the following mechanisms. Primarily the wire is gripped by deformation, through compression between the pin i) and the slotted nose 151. The compressive force is furnished through the toggle joint mechanism consisting of balls 152, rods 153, and adjustment screw 154, the joint itself loaded in the down position as shown in Figures 25 and 26 by the presser bar 155 through the spring 156. When the toggle joint is released, shown dotted in Figure 25, the pin 150, carried in nose 151 mounted to the head structure 157 with screws 158, is retracted by the spring 159, to release the wire preparatory to receiving a fresh strand for a new tie, in an action hereinafter described.

The adjustment screw 154, locked against vibration through plug 16) and screw 161, permits the relative positioning of the toggle mechanism in the loaded condition, to adjust for diiferent diameter wire sizes and desired gripping forces. The tightest gripping action of the toggle mechanism is obtained when the joint is very nearly flat in the loaded position.

The presser bar 155, raised and lowered to release or grip the wire strands through an action hereinafter described, carries pin 162 in its lower end extending up through the inside of spring 155, through the head structure 157, into contact with the center ball 152 of the toggle joint, thus insuring that, as the presser bar is raised, the joint itself will break and follow upwards, into the dotted position shown.

The toggle joint is released, i. e., the pin retracted to release the wire, by the upward movement of the presser bar 155. The presser bar carries a beveled slot or groove 237 notched in its side, seen in Figure 23. With the gripper head retracted back behind the wire line, as pictured at N, Figure 23, the pawl 163 pivoted at 164, is held in engagement with the notched bar 155 by leaf spring 165. As the gripper head is advanced out across the wire line through the drive mechanism heretofore described the pawl support structure 166 pivoted at 167, is prevented from moving by the pawl stop member 168, resulting in its pivoting about 167, raising the pawl pivot point 164, and in turn raising the presser bar 155 to release the toggle joint and retract the pin 150. Thus, each time the gripper head is driven forward, preparatory to receiving the wire as it is laid about the bundle by the wire-laying rings, the gripping mechanism is released and prepared to receive the wire.

Wire enters the gripper nose 151 and is drawn up and under the toggle loading finger 170, lifting the finger to load the toggle joint and grip the wire. The lifting by the wire of finger 170, connected to pawl throwoff 171 through rod 172 carrying adjustment nuts 173 and 1'74, pivots the throwoff 171 about 167 to engage the extended inner surface of the pawl 163, pushing the pawl back, against spring 165, about pivot 164, to disengage the pawl and presser bar, as shown at N, Figure 23. This allows the presser bar 155 to snap down, through the action of spring 156 to load the toggle joint and drive pin 150 forward to positively and securely grip and hold the wire in the gripper head nose.

Finger 170 is spring loaded through spring 175 to insure its falling down preparatory to being actuated by the wire entering the nose. The pawl support structure 166 carries pin 176 and is spring loaded through 179 to insure its remaining in intimate contact with adjustment screw 169, thus reestablishing the engagement of pawl 163 in the notched bar 155, as the gripper head is retracted through the drive mechanism.

Each gripper head carries the lever 177, supplied with handle 178, and pivoted in such a manner that, when pulled forward by hand the presser bar 155 is raised, independent of the pawl mechanism, to retract the pin 150 and permit loading the gripper head by hand, as is re quired with the initial installation of a coil of wire.

Referring to Figures 21, 22 and 27, each gripper head carries a fixed cutter block 180, mounted on the inside, or twister head side, of the gripper nose, so that as the wire is reversed within the gripper head and wrapped around the bundle, as at K, the wire is drawn up into the cutter block deforming the torsion spring 181, as indicated in Figure 30, for a purpose hereinafter described. Also, as the wire is laid around the bundle and crosses over into the gripper head as at K, it must also enter the cutter block 180, again deforming the torsion spring 181 mounted in a slot between the cutter block and the gripper head structure.

Referring to Figures 18, 2], 22 and 24, the wire has been laid about the bundle 14, gripped on both sides of the twister head, which lies back behind the wire line, as at I, Figure 21. The twister head must be driven out, as at L, Figure 21, to pick up the crossed wires in the slotted twister gear preparatory to knotting. Cylinder C4 drives the plate cam 182 out, perpendicular to the axis of the twister heads, engaging cam followers 183 mounted on the twister head structure 184, to move both front and rear heads out simultaneously, across the wire lines, piclo ing up the wire binding strands in the slotted twister gear 185. Figure 24, for the sake of clarity shows the right hand, or rear twister head, out, as at L. Figure 21 shows the left hand, or front head, retracted, as at J. The twister heads slide in dovetail bearings, members 148 engaging mating dovetail slots M in the structure 149, similar to the gripper heads.

Limit switches LS8 and L811, their functions hereinafter described, are mounted on the structure 149 as shown, Figures 18, 21 and 23, and are actuated through suitable cam detents by the motion of the plate cam 182.

Referring to Figures 19, 21 and 24, the twister head drive pinion 186 carried in the twister head structure 184, slides on the square-ended twister drive pinion shaft 187 during the motion of the twister heads in and out.

Referring to Figures 18, 19, 20, 21 and 24, the wire strands are twisted to form the start of the knot, Figure 32, by the rotation of the slotted twister gear 185. Cylinder C rotates the twister drive pinion 186 through the square-ended shaft 187, the bevel gears 188, 189, and the jack shaft 190, by driving the rack 191, meshed with gear 12 192, keyed to shaft 190 by 193, upwards. The twister gear is driven by gear 194 integral with bevel gear 195 meshed with the twister drive pinion 186.

At the top of the stroke of C5, the twister gear having been rotated 4 /2 revolutions, the limit switch LS9 is actuated by the cam 196 on the rack 191, to reverse, through the control system hereinafter described, the direction of motion of the cylinder C5, and hence the direction of motion of the twister gear, untwisting the knotted tie a slight amount, to reduce its strains, as heretofore brought out.

The rack 191 is driven downward until the pawl stop 197, carrying limit switch L510, held in contact by the spring action of the single-acting cylinder C6, engages the beveled, notched slot cut in 191, to halt any further downward motion of the rack, and thus stop any further rotation of the twister gear 185. This twister gear stops during its reverse turning in the open position, having rotated /2 revolution from the 4 /2 position to the 4 position, preparatory to spilling the finished knotted tie out of the slot.

Referring to Figures 24, 27, 28 and 29, the shaft 199 common to the bevel gear and gear 194 also carries the cutting cam 198, keyed to the shaft (the key not shown). The rotation of the gear 194 through the twisting drive mechanism heretofore described, rotating commonly with the cam 198, and through the correct timing acts to pivot the bell crank 200, carrying a cam follower 201, to the position shown dotted in Figure 29. The bell crank 200, keyed to the shaft 202 passing through the twisting head 184, acts in common with lever 203 located on the opposite side of the twister head and also keyed through 204 to the same shaft. As the twister head is driven forward to pick up the wire strands for twisting the bell crank 200 and the lever 203, carrying rollers 205 move forward to a position, shown dotted in Figures 27 and 28, of the roller, under the cutting slide 206 on the gripper heads on each side of the twister head. The motion of the rollers 205 upwards due to the cam 198 raises the cutting slide 206, retained in the gripper head structure 157, and spring-loaded by compression spring 207. The crank 208, pivotally mounted at 209, and carrying roller 210 in cutting slide 206, levers forward during the upward motion of slide 206 to hinge the pivotally mounted cutting bar 211, forward across the cutter block 180, as shown dotted in Figure 27, to cut, by shearing between 211 and 180, the wire strand extending from the gripper head through the cutter block, in front of the cutting bar and to the wire twist. The spring 207 serves to return the cutter mechanism to the normal, in, position as shown in full in Figure 27, after the cam 198 has rotated past the high point of the rise.

This cutting action takes place, through the correct gear timing, between 3 and 3 /2 twists of the wire strands by the twister gear. After the cut takes place the further full rotation of the twister gear serves to wrap the severed end of the twisted wire knot under by rubbing against the cutter bar 211, to produce a finished knot as shown in Figure 32.

The cutting of the gripped wire ends through the action described above severs completely the tied knot, and the retraction of the twister head, which has the slotted twister gear in the open position, back behind the wire line, causes the knotted wire to spill out of the slotted gear and snap free up against the under side of the now wire-tied bundle supported on table 28.

During each cycle of the machine one of the gripper heads on each face, front and rear, of the machine will end up, after the twisting and cutting action has taken place, with a small, hairpin shaped clip retained within the head, as shown in Figure 22. This head is always behind the wire line, and, as the head is carried forward during the next cycle to receive the next strand of wire for gripping for a new tie the toggle mechanism is released, the pin withdrawn within the gripper nose, and the small clip is free to fall out, to clear the gripper head. The clearing of the head is fa .ilitated by the small torsion spring 181, heretofore described, which is elevated by the wire as it is drawn up into the gripper nose during the wire-laying cycle, as pictured in Figure 30. Release of the wire clip by the toggle mechanism permits the piece to fall free, aided by the spring action of 181, the clip caught within trays 212 located underneath the gripper heads on each side of the machine, Figures 18 and 19. Figure 31 shows the spring 181 in position after clearing the gripper head and before the new wire strand has been laid into place.

The retraction of the twister head to spill the completed tie and complete the bundling operation actuates, through the electrical control system hereinafter described, the reset mechanism, which controls cylinder C6, Figure 18, causing it to pull the pawl stop 197 out of engagement with the rack 1%1, permitting the twister gear to return to its normal, open, position through the final downward travel of the cylinder C5. At the same time, the compressor head 28, and the straightener head 11 are retracted to further release the bundle and permit its removal from the machine, either by the machine operator or by the motorized powered conveyor tables. The machine thus is prepared for further tying on successive bundles, each tying operation being a repeated performance of the action outlined above.

Referring to Figures 1 and 3, the main structure consists of the center frame 1, the left side frame 213, which has cast integral with it a cavity for the mounting of the electrical control system; the right side frame- 214 and the base 612, which is covered across the bottom by plate 215 to form a receiver for the exhaust air of the pneumatic system, as hereinafter described. The center plate 1 carries the structure 142 that supports the tying mechanism, as heretofore described. The machine openings are enclosed with sheet metal covers, access doors, and plates (not shown), to present a complete, presentable unit.

Referring to Figure 33, the pneumatic system of the wire-tying machine has been pictured for the sake of clarity as a line diagram. The location and installation of the electrically operated valves and pneumatic accessories are not shown on the detailed views of the machine. The main air supply enters the machine through the shutoff plug valve 216, and flows through filter 217, regulator 218, and lubricator 219 before passing into the main supply lines to the various pneumatic drive components. A conventional pressure sensitive switch PS1, hereinafter described, is located at the filter and lubrication point.

The straightener head 11 is driven by the single-acting spring return cylinder C1, controlled by the electrically operated 3-way valve V1.

The compressor head 28 is driven by the double-acting cylinder C2 controlled through the electrically operated 4-way S-port valve, V2, the return pressure regulated through regulator 22d, and the speed in both the up and down directions by the flow control valve 221.

The main drive rack 511 is driven through the doubleacting, double rod-ended cylinder C3, controlled by the electrically operated, double solenoid 4-way 4-port valve V3. The supply pressure to V3 can be switched from high to low, as heretofore described, by the parallel system consisting of regulators 221 and 222, and the twoway electrically operated valves V9 and V10.

The twister head drive plate 192 is driven by the doubleacting cylinder C4 controlled by the 4-way electrically operated valve V4, the exhaust air not being returned to the base receiver, but mufiled through 223 to the atmosphere.

The twist and cut rack 191 is driven by the doubleacting cylinder C5, controlled by the electrically operated 4-way S-port valve V5. The return supplypressure to C5 is reduced from themain air supply pressure to C5 through regulator 224.

The pawl stop 1.97 is driven by the single-acting, springreturn cylinder C6, controlled through the electrically operated valve V6, the exhaust muffled through 225 to the atmosphere.

The main and reversing clutch yokes 164 are driven through the double-acting cylinders C9 and C10 respectively, controlled by the electrically operated 4-way valves V11 and V12 respectively.

The front and rear slack takeup cylinders C7 and C8 respectively, are controlled through the 3-way valves V7 and V8 respectively, the supply pressure regulated from the main air supply manifold through 226 and 227 to produce the desired cylinder pressures for correct wire tensioning. The exhaust air is controlled by the flow control valves 228 and 229, and muffled tothe atmosphere through 230 and 231. The flow control valves are used to create the desired back pressure in the slack takeup cylinders. The pressure sensitive switches PS2 and PS3 are used as part of the control of the valves V7 and V8, in that, as the wire is taken from the slack take up and the sheaves reduced towards one another the cylinder pressure will increase. These switches act upon this increased pressure to cut out V7 and V8 and exhaust the cylinders C7 and C8, to afford the control of the Wire tension during the wire-layingcycle, as heretofore described.

All of the exhaust lines from those valves not exhausted to the atmosphere through mufflers are led to the exhaust receiver, built into the base of the machine by 60 and 215,

' and thence are led away from the machine in one single line, to complete the silencing of the pneumatic system.

ELECTRICAL CONTROL SYSTEM The electrical control system is broken down into two parallel circuits, the automatic circuit and the hand circuit. The automatic circuit provides for the proper sequencing of tying operations, one after the other, utilizing a number or" safety devices and interlocking controls. The hand circuit is intended for use as a means of individually testing the pneumatic system and attendant mechanisms. It is not intended to be used as means of hand sequencing the tying operation.

1. Main power contactor circuit A. P0wer-A. C. or D. C.of any of the conventional voltages, is brought into the machine at L1 and L2 through fuses F1 and F2. The main power contactor (CR1) is controlled through the main control switch (S1), a three position selector switch, as indicated:

(1) in the Off position the entire electrical system is disconnected.

(2) In the Automatic position CR1 is controlled through pressure switch PS1. If the main air supply line is up to operating pressure CR1 is actuated and the rest of the control system is connected into L1 and L2 through the two contacts of CR1, CRM and CRlb.

(3) In the Hand position, hand operation contactor (CR2) is energized, which in turn actuates CR1 through contact CRZa, independent of the air supply pressure.

2. Straightener circuit A. The straightener contactor (CR3) is controlled through the straightener set switch (S2), the foot treadle switch (PS), and the two bundle position switches (LS1) and (LS2). These serve the following function:

(1) Straightener set switch (S2), a two-position selector switch, is used to drive the straightener head 11 out, so that the mechanical adjustments to its stroke may be effected. In the Run position it supplies primary power (L1) to the foot switch.

2) The foot treadle switch (FS) is the primary means of initiating the tying operation. It is by-passed by the automatic, initiating circuit (see 14C below), used when 15 the optional automatic feed equipment is installed. This common junction is also used for primary energization of the slack takeup control (see 9Cla below).

(3) The bundle position switches (LS1) and (LS2) are used to indicate the presence of a bundle 14 within the wire-laying rings 21 and 29. LS1 is located in the front table F, just below the front ring 29, and LS2 is located in the rear table 9, just after the rear ring 21. These circuits render it possible to initiate the wirelaying and tying circle without a bundle properly in position.

(4) These two switches also serve to indicate the presence of a low bundle, i. e., a bundle too low for satisfactory bundling and shipping, through the stitfness of the spring-loaded plungers actuating the switches, gaging the bundle size by weight.

B. LS2 is by-passed by the parallel circuit consisting of the two normally closed contacts CRl9d and CR20c. When single ties are being made both contactors CR19 and CR20 are de-energized, so that the bundle to be tied does not necessarily need to extend through the second, rear, wire-laying ring 21, in order for the machine to be operated.

C. Contactor CR3 is electrically locked in through the holding contacts CRlla and its own contacts CRSa. After energization through FS, CR3 is maintained until holding contactor CR11. is actuated.

D. The straightener cylinder valve (V1) is controlled through:

(1) Contact CR3b.

(2) Straightener set switch S2, if switched to the set position. 7

(3) Straightener hand test switch S3, a push-button station for hand operation of the straightener system.

This station, and its circuit is inoperative unless contact CRZB is closed, through the main control switch.

3. Compressor circuit A. The compressor contactor (CR4) is controlled through the contacts CR3c and side position switch LS3. This makes it impossible to energize CR4 without:

(1) The straightener contactor, and hence the straightener head 11, being actuated.

(2) The bundle being tied being located up against LS3, indicating that the bundle has been racked up against the side bars 15.

B. CR4 is electrically locked in by holding contact CRlla and its own contact CR4a. Thus, if the bundle being tied is moved away from LS3 at any time during the tying cycle CR4 will not fall out and the compressor head lift up. After initial energization through LS3, CR4 is maintained until CRll is actuated.

C. The compressor cylinder valve (V2) is controlled through:

(1) Contact CR4b.

(2) Compressor hand test switch (S4), a push-button station. This station, and its circuit, is inoperative unless contact CR2b is closed.

4. Main drive circuit A. The main rack drive contactors, left and right, CR5 and CR6, respectively, are controlled through CR4c, drive position limit switch (LS4), and the contacts CR6a and CRSa.

l) Energization of the compressor contactor RC4, to initiate the compressor head 18 down, closes CR4c to supply primary L, power to the parallel main drive contactor circuits.

(2) Depending upon the position of the main drive rack 50, LS4 will have its contact either open or closed. (a) If the drive is to the left, LS4 is closed, and NO contact is closed, and CR5, the left main drive contactor, is energized. (b) If the drive is to the right, LS4 is open, and CR6, the right main drive contactor, is energized.

(3) The main rack cylinder valve (V3) is a double solenoid momentary-action type valve, coil V3a shifting the valve spool to drive the piston to the right, and V311 to drive the piston to the left. (a) The main rack 50 is driven to the right through energization of V3a by CRSb. CRSb is closed only when the drive position switch LS4 is actuated, indicating that the rack must, on the next stroke, be moved to the right. (b) The main rack is driven to the left through energization of V3b by CR6b. CR6b is closed only when the drive position switch LS4 is open, i. e., the normally closed contact is closed, indicating that the rack must, on the next stroke, be moved to the left.

B. CR5 is electrically locked in through its own contact CRSc so that, as the gripper head drive arm moves oft" LS4 the contactor will remain closed.

C. CR6 is electrically locked in through its own contact CR6c so that as'the gripper head drive arm moves on LS4 the contactor will remain closed.

D. Both CR5 and CR6 are isolated from their main controlling circuits by each others contacts, CR5 by CR6a and CR6 by CRSa. This is so that, upon energization of either CR5 or CR6 the corresponding opposite drive contactors cannot be actuated without first opening CR- lc. This prevents the drive from continuous cycling.

E. Contactor CR5 or CR6 can be hand actuated through hand test switch S5, a push-button station. This station, and its circuits, is inoperative unless contact CR2b is closed.

5. Twister head drive circuit A. Holding contactor (CR7) is used to prevent premature operation of the twister and brake contactors, and is controlled through the drive position limit switch (center) LS5.

(1) CR7 is electrically locked in through CRllb, and its own contact CR7a. Upon actuation of LS5, CR7 will remain energized until actuation of CR11.

B. The twister head drive contactor CR8 is energized through any one of three circuits:

(1) Main circuit, through contact CR7b and the parallel limit switch circuits of the drive position switches LS6 and LS7. (a) CR7b is used to prevent premature energization of CR8 by either LS6 or LS7, as might be the case when the drive reverses itself for each succeeding cycle, due to cam orientation. (b) LS6 and LS7 are limit switches indicating the approaching end position of the main drive. They are separated and in parallel to afford the opportunity of energizing the twister head drive contactor at the earliest possible moment (through proper cam 69 orientation on the main pinion shaft 61).

(2) Post loading circuit. When threading the machine by hand as required when a new coil of wire is used, the twisting and cutting mechanism must be actuated, independent of the rest of the equipment, to cut and remove the tail-end piece of wire. Post loading switch S6, a push-button station, by-passes the straightener, compressor, and main drive circuits to actuate the twister head drive mechanism, and thus initiate the twisting and cutting operation.

(3) Hand operation circuit. Contact CRlSa is part of the hand operating circuit of the twisting and cutting mechanism. In the hand operation of this mechanism the twister head is driven out through this circuit.

C. CR8 is electrically locked in through holding contact CRllb and its own contact CRSa. Thus the twister head will remain in the out position until holding contactor CR1]; is energized to break the holding circuits of both CR7 and CR8.

D. The twister head cylinder valve (V4) is controlled through:

(1) Contact CRSb.

(2) Hand operation switch S7, a push-button station. This station, and its circuit, is inoperative unless contact CR2b is closed. 

